Heat exchanger

ABSTRACT

A heat exchanger includes a bundle of tubes, which can be inserted into a tubular housing. Exhaust gas can flow through the tubes. A coolant duct can be arranged between the tubes. The bundle of tubes can have at least one grid-like securing structure which supports the bundle in the housing. The behavior of the heat exchanger with respect to vibrations is affected by outwardly curved metallic springs attached to the bundle of tubes which may be deformed in the opposite direction to the insertion direction of the bundle into the housing. The spring force is directed against the housing in order to dampen vibrations. The heat exchanger can also include an elastic device for permitting a change in length caused by temperature changes.

RELATED APPLICATIONS

The present application is a continuation-in-part of and claims priorityto U.S. patent application Ser. No. 11/764,491, filed Jun. 18, 2007,which claims priority to German Patent Application No. 10 2006 028578.6, filed Jun. 22, 2006, and is a continuation-in-part of and claimspriority to U.S. patent application Ser. No. 12/696,986, filed Jan. 29,2010, the entire contents of all of which are hereby incorporated byreference.

FIELD OF THE INVENTION

The present invention relates to a heat exchanger, such as, for example,an exhaust gas heat exchanger.

SUMMARY

An exhaust gas heat exchanger is known from EP 1 348 924 A2 and from EP1 544 564 A1. These heat exchangers have essentially fulfilled theirintended functions. However, recently, exhaust gas mass flows, and alsoexhaust gas temperatures of motor vehicle engines and consequently alsothe thermal stresses experienced by exhaust gas coolers have risen.These changes can cause fractures and similar damage caused byexcessively high temperature change stresses and can result in thesystem failing.

Consideration has also been given to improving exhaust gas heatexchangers in terms of their ability to withstand temperature changestresses. Such a solution is known, for example, from WO 03/036214A1. Inthis document, slits and a folding bellows have been arranged in thehousing, as a result of which, the expansion behavior of the individualparts of the exhaust gas heat exchanger can be reliably improved. WO03/064953 has, on the other hand, provided an expansion bead in thehousing casing. WO 2003/01650 has proposed a sliding seat arrangement.All these solutions appear to be expedient without, however, being ableto meet all of the requirements of current applications.

DE 32 42 619 A1 also discloses a heat exchanger having a grid-likesecuring structure, which performs the function of directing orinfluencing the flow in the housing. Furthermore, elastic elements areprovided on the securing structure which are intended to compensate, andcan compensate for the specific tolerances in the housing into which thetube bundle is inserted. For this reason, they are formed from asuitable plastic material which can be deformed in the wide regions andwhich therefore permits relatively large tolerance ranges. The elasticelements are attached to the securing structure, which is made of metal.The vibration-damping properties of the elastic element may be presentbut they are not sufficiently effective. Furthermore, in particular, inheat exchangers with a considerable length, vibrations which can only beadequately dealt with by means of the known elastic elements which occurat other locations. U.S. Pat. No. 3,804,161 also discloses heatexchangers.

In some embodiments, the present invention provides a heat exchangerwhich can make a contribution to solving one or more of the problemsoutlined above. The present invention can also or alternatively reducevibration levels.

Because a grid-like metallic securing structure is embodied in one piecewith elastic hook-shaped protrusions which point toward the inside ofthe housing and which are deformed in the opposite direction to theinsertion direction of the bundle into the housing and whose springforce is directed against the housing in order to reduce the vibrationlevel, and because a device which permits and compensates for changes inlength and which has elastic properties is embodied and provided by thepresent invention, vibrations of the bundle in the housing can besignificantly reduced and/or damped. The changes in length or changes inshape are induced by changes in temperature which occur during theoperation of the heat exchanger. In principle, the natural frequency ofthe bundle is raised.

The deformed elastic hook-shaped protrusions can project over thecross-sectional surface of the housing before the bundle is insertedinto the housing. When it is inserted, the elastic hook-shapedprotrusions can be elastically deformed counter to the spring force inorder to fit into the housing and in order then to apply this springforce against the inside of the housing.

Alternative proposals for a solution are provided by individual elasticmetallic hook-shaped protrusions or springs which are attached to ametallic securing structure or between two metallic securing structures.

Within the scope of their investigations, the inventors have arrived atthe conclusion that, in some applications, it is insufficient to providesuch elastic, metallic hook-shaped protrusions or springs or the like.For this reason, they additionally provide a device which compensatesfor changes in length of the bundle and of the housing which are inducedby changes in temperature, and they also embody this device with elasticproperties in order to promote the vibration reducing property of theentire device.

In some embodiments, the present invention also provides for the housingto be composed of aluminum and to be embodied as a cast part into whichthe bundle, which can be a stainless steel soldered structure, can beinserted with tube plates, which are provided on the tube ends, and adiffuser.

The housing can have a connecting flange which can be matched to thediffuser, the device which permits changes in length having an elasticseal between the diffuser and the connecting flange.

In some embodiments, the present invention can include an elastic sealarranged in at least one groove, or alternatively, positioned to fillsubstantially the entire region between the diffuser and connectingflange.

In some embodiments, the present invention provides at least oneclamping element, which extends through the bundle and is arrangedbetween two grid-like securing structures in order to dampen vibrations.In some such embodiments, a device which permits changes in length andwhich has elastic properties is also provided.

The tubes can be constructed as flat tubes which can be composed ofpairs of plates and/or can be manufactured from a sheet metal strip andwelded to a longitudinal seam. Round tubes which extend as tube bundlesstraight through the heat exchanger in a manner similar to that shown inDE 32 42 619 A1 can also or alternatively be used. However, in order toimprove the exchange of heat, these tubes can have a twist whichprovides the tube wall with a corrugation.

Emission concerns associated with the operation of internal combustionengines (e.g., diesel and other types of engines) have resulted in anincreased emphasis on the use of exhaust gas heat exchange systems withsuch engines in vehicular and non-vehicular applications. These systemsare often employed as part of an exhaust gas recirculation (EGR) systemin which a portion of an engine's exhaust is returned to combustionchambers via an intake system. The result is that some of the oxygenthat would ordinarily be inducted into the engine as part of its freshcombustion air charge is displaced with inert gases. The presence of theinert exhaust gas typically serves to lower the combustion temperature,thereby reducing the rate of NO_(x) formation.

In order to achieve the foregoing, it is desirable for the temperatureof the recirculated exhaust to be lowered prior to the exhaust beingdelivered into the intake manifold of the engine. In many applicationsemploying EGR systems, exhaust gas recirculation coolers (EGR coolers)are employed to reduce the temperature of the recirculated exhaust. Inthe usual case, engine coolant is brought into heat exchange relationwith the exhaust gas within the EGR cooler in order to achieve thedesired reduction in temperature. The use of engine coolant providescertain advantages in that appropriate structure for subsequentlyrejecting heat from the engine coolant to the ambient air is alreadyavailable for use in applications requiring an EGR system.

In some applications, however, the temperature to which recirculatedexhaust must be lowered in order to achieve the desired reduction in therate of NO_(x) formation is lower than, or appreciably close to, thetemperature at which the engine coolant is regulated by the engine'sthermal management system. In such cases, a second EGR cooler may beemployed to extract from the recirculated exhaust that portion of thedesired heat load which cannot be readily transferred to the enginecoolant at its regulated temperature. This second EGR cooler (frequentlyreferred to as a “low temperature EGR cooler” or “LT EGR cooler”)commonly receives either a flow of coolant from a separately regulatedcoolant loop, or a portion of the regular engine coolant loop which hasbeen cooled to a lower temperature.

Packaging the LT EGR cooler along with an EGR cooler (sometimes referredto as the “high temperature EGR cooler” or “HT EGR cooler”) can beproblematic due to space constraints. Placing both EGR coolers into acommon casing can help to ease these packaging issues, but can make itmore difficult to accommodate the differences in thermal expansionbetween the exhaust gas conveying tubes in the EGR coolers and thecasing. Such thermal expansion differences have been known to lead topremature failure of the heat exchanger.

Although applications involving EGR cooler connections (to other EGRcoolers and/or other structures) illustrate the design challengesdescribed above, such challenges exist in other heat exchangerapplications as well—some of which involve heat exchangers outside ofexhaust gas recirculation technology. Based upon these and otherlimitations of conventional heat exchanger connection designs, improvedheat exchanger connections and connection methods continue to be welcomein the art.

In accordance with some embodiments, of the present invention, a heatexchanger includes a casing having a proximal end and a distal end, witha fluid flow path extending from the proximal end to the distal end. Theheat exchanger further includes a plurality of heat exchange tubesdefining a first section of the fluid flow path extending from theproximal end, and another plurality of heat exchange tubes defining asecond section of the fluid flow path extending to the distal end. Athird section of the fluid flow path fluidly connects the first sectionto the second section, and includes at least one sealing plate. The heatexchange tubes defining the first section are rigidly attached to thecasing at the proximal end, and are structurally decoupled from thecasing at their opposite ends. The heat exchange tubes defining thesecond section are rigidly attached to the casing at the distal end, andare structurally decoupled from both the casing and the heat exchangetubes defining the first section at their opposite ends.

Another feature of the present invention includes a casing having apocket containing at least a portion of the sealing plate. The pocket isdefined by a planar wall that provides a sealing surface for afluid-tight seal between the casing and the sealing plate, and by one ormore peripheral walls that bound the outer periphery of the planar wall.The pocket may be further defined by another planar wall that isparallel to and spaced apart from the first planar wall. This secondplanar wall can provide a sealing surface for a fluid-tight seal betweenthe casing and a second sealing plate.

In some embodiments, the third section of the fluid flow path includes agroup of one or more cylindrical flow conduits rigidly attached to theheat exchange tubes defining the first section, and a group of one ormore cylindrical flow conduits rigidly attached to the heat exchangetubes of defining the second section. At least one of the groups extendsat least partially into the pocket in the casing. As one feature,fluid-tight seals extend around one or more of the cylindrical flowconduits and allow for movement in the axial direction relative to thecasing. The first and second groups of cylindrical flow conduits may beseparated from one another in order to accommodate thermal expansiondifferences between the heat exchange tubes and the casing.

In some embodiments of the present invention, the heat exchangerincludes a second fluid flow path passing over the heat exchange tubesdefining the first section, and a third fluid flow path passing over theheat exchange tubes defining the second section. The second and thirdfluid flow paths are sealed off from the first fluid flow path by atleast some of the fluid-tight seals in the third section of the firstfluid flow path. In some cases the second and third fluid flow paths arenot in fluid communication with one another within the heat exchanger.

In some embodiments of the invention the heat exchanger may be used asan EGR cooler, with a recirculated exhaust gas flowing along the firstflow path, a first flow of coolant flowing along the second flow path,and a second flow of coolant flowing along the third flow path. In somecases one of the flows of coolant may be at a lower temperature than theother flow of coolant.

In accordance with some embodiments of the present invention, a heatexchanger includes a casing having a proximal end and a distal end, witha fluid flow path extending from the proximal end to the distal end. Theheat exchanger further includes a first plurality of heat exchange tubesdefining a portion of the fluid flow path including the proximal end,and a second plurality of heat exchange tubes defining a portion of thefluid flow path including the distal end. A flow transitioning structuredefines the fluid flow path between the distal end of the firstplurality of heat exchange tubes and the proximal end of the secondplurality of heat exchange tubes, and structurally decouples the distalend of the first plurality of heat exchange tubes from the proximal endof the second plurality of heat exchange tubes.

In some embodiments, the casing includes a pocket containing at least aportion of the flow transitioning structure. The pocket is defined by aplanar wall that provides a sealing surface for a fluid-tight sealbetween the casing and the flow transitioning structure, and by one ormore peripheral walls that bound the outer periphery of the planar wall.The pocket may be further defined by another planar wall that isparallel to and spaced apart from the first planar wall. This secondplanar wall can provide a another sealing surface for anotherfluid-tight seal between the casing and the flow transitioningstructure.

Other independent aspects of the invention will become apparent byconsideration of the detailed description, claims and accompanyingdrawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 shows a perspective view of a cut open exhaust gas heatexchanger.

FIG. 2 is a detailed view showing a piece of the tube bundle with asecuring device.

FIGS. 3-4 are similar to FIG. 2 but with modified securing devices.

FIGS. 5-6 are detailed views of the heat exchanger with a clampingdevice.

FIGS. 7-9 show details of the heat exchanger in the region of theelastic device.

FIG. 10 is similar to FIG. 4 but with modified spring devices.

FIG. 11 is a perspective view of a heat exchanger according to anembodiment of the present invention.

FIG. 12 is a perspective view of a heat exchanger core for use in theheat exchanger of FIG. 11.

FIG. 13 is a perspective view of a tube and insert for use in the heatexchange core of FIG. 12.

FIG. 14 is a perspective view of a casing section of the heat exchangerof FIG. 11.

FIG. 15 is another perspective view of the casing section of FIG. 14.

FIG. 16 is a partially exploded and partially cut-away perspective viewof a portion of the heat exchanger of FIG. 11.

FIG. 17 is a cut-away perspective view of a sealing plate for use in theheat exchanger of FIG. 11.

FIG. 18 a is a sectional detail view of the heat exchanger of FIG. 11,taken along lines XVIII-XVIII of FIG. 11.

FIG. 18 b is a sectional detail view of the heat exchanger of FIG. 11according to an alternative embodiment of the present invention, alsotaken along lines XVIII-XVIII of FIG. 11.

FIG. 19 is a schematic representation of an engine system including aheat exchanger embodying the present invention.

FIG. 20 is an exploded view of a spring plate and attachment structure.

DETAILED DESCRIPTION

Before any independent embodiments of the invention are explained indetail, it is to be understood that the invention is not limited in itsapplication to the details of construction and the arrangement ofcomponents set forth in the following description or illustrated in thefollowing drawings. The invention is capable of other embodiments and ofbeing practiced or of being carried out in various ways. Also, it is tobe understood that the phraseology and terminology used herein is forthe purpose of description and should not be regarded as limiting. Theuse of “including,” “comprising,” or “having” and variations thereofherein is meant to encompass the items listed thereafter and equivalentsthereof as well as additional items. Unless specified or limitedotherwise, the terms “mounted,” “connected,” “supported,” and “coupled”and variations thereof are used broadly and encompass both direct andindirect mountings, connections, supports, and couplings. Further,“connected” and “coupled” are not restricted to physical or mechanicalconnections or couplings.

The block arrows in FIG. 1 indicate the direction of flow through theexhaust gas heat exchanger, with the black block arrows being intendedto symbolize the exhaust gas and the block arrows without fillingsymbolizing the cooling fluid flow. The illustration as doubled blockarrows is intended to indicate that the media can flow through theexhaust gas heat exchanger in either a parallel flow manner or in acounter flow manner. Corresponding inlets and outlets 80, 70 areprovided. The corresponding arrows in FIGS. 1 and 2 which point in thelongitudinal direction of the heat exchanger show the insertiondirection of the tube bundle into the housing 11.

The tube bundle of the heat exchanger includes a plurality of tubes 2which are formed as drawn flat tubes 2 in the exemplary embodiment. Inthe illustrated embodiment, each flat tube 2 contains a turbulator 3. Ineach case a coolant duct 5, which can be equipped with flow directingelements, can be arranged between two flat tubes 2. No such elements areshown in the figures, but the coolant ducts 5 are of rather flat design.In the exemplary embodiments, two rows 2.1 and 2.2 of flat tubes 2 havebeen provided. As is apparent from FIG. 4, there are six flat tubes 2 ineach row.

The tube bundle in FIG. 1 has a plurality (i.e., five) of grid-likemetallic securing devices 10, with just one of them (in the exemplaryembodiment) having been equipped integrally therewith sprung hook-shapedprotrusions 12 which are arranged on opposite sides of the securingdevice 10 or of the tube bundle. Depending on the length of the heatexchanger and/or according to other influencing factors, a correspondingselection of securing devices 10 can be embodied integrally with sprunghook-shaped protrusions 12. Instead of one-piece hook-shaped protrusions12 it is also possible to provide springs 12 b or the like as individualparts which are to be attached to the securing devices 10 in africtionally and/or positively locking fashion.

Two exemplary embodiments which show sprung, metallic hook-shapedprotrusions 12 as individual parts, which are attached in a frictionallyand positively locking fashion to grid-like, metallic securing devices10, have been represented in FIGS. 3 and 4. From the figures, inparticular from FIG. 2, it is also clear that the sprung, metallichook-shaped protrusions 12 are deformed in the opposite direction to theinsertion direction in order to facilitate the insertion.

In FIG. 2, the position of the hook-shaped protrusions 12 beforeinsertion into the housing 11 which is not shown there was indicated ina basic fashion using the example of a single hook-shaped protrusion 12by dashed lines. The hook-shaped protrusions 12 are arranged on oppositesides. The hook-shaped protrusions 12 therefore protrude somewhatfurther from the virtual center of the heat exchanger and are forced, asthe tube bundle is inserted into the housing 11, during which processthey move in a sprung fashion toward the center and undergo a change inshape which occurs within the elastic region. The spring force of thehook-shaped protrusions 12, which is built up in the process, then actsagainst the housing wall and ensures, through interaction with thehook-shaped protrusions 12, which are arranged on opposite sides, thatthere is a corresponding reduction in the vibrations which occur duringoperation of the heat exchanger, for example in a motor vehicle.

Irrespective of whether hook-shaped protrusions 12 are provided or not,the grid-like securing devices 10 can, for example, be in two parts,with the parts being pushed in a comb-like fashion from opposite sidesover the flat tubes 2 or being pushed in one part and then from one endof the tube bundle in its longitudinal direction as far as the positionprovided. The grid rods are intended at any rate to extend through thecoolant duct 5.

A tube plate 30 and a collecting box for a diffuser 31 are fitted onboth ends of the tube bundle. The diffuser 31 changes the geometry onthe exhaust gas side from a four corner shape at the tube plate 30 intoa round shape at the connecting flange 60 (see below). One or more ofthe aforementioned components can be manufactured from stainless steel.The described structure can be connected to form one physical unit in ahard soldering process. However, when springs or the like are providedas individual parts they can also be attached to the securing device 10after the soldering.

The soldered physical unit can then be inserted into a housing 11 (withthe diffuser 31 at the front) in the insertion direction indicated bythe aforementioned arrow, and can be completely mounted.

The housing 11 can be a cast structure made of aluminum. It can have aconnecting flange 60 for the exhaust gas which is dimensioned in such away that the diffuser 31 which is soldered onto the tube bundle by meansof a tube plate 30 fits and is received therein. In addition, a groove61 can be formed in which an elastic sealing ring or some other suitableseal 62 can be located (see FIGS. 7-8).

FIG. 8 shows an enlarged detail from FIG. 7. From this illustration itis clear that changes in length caused by changes in temperature can becompensated for by permitting movements in the longitudinal direction ofthe tube bundle or of the housing 11. The two doubled block arrows inFIG. 9 are intended to indicate this. In FIG. 9, in order to form theelastic properties of the device 20, the entire annular gap regionbetween the diffuser 31 and the connecting flange 60 has been providedwith an elastic rubber ring 62 or the like—instead of the two O-rings 62in the groove 61 according to FIGS. 7 and 8. Here, improved elasticproperties can be expected. The existing annular gap can be somewhatlarger here, viewed in the radial direction, than in the exemplaryembodiment according to FIGS. 7-8.

The formation of sliding seats which are present in the prior art and inwhich metal is usually slid on metal is avoided by means of thisproposal, with the aim of improving the vibration behavior of the heatexchanger. As is shown further by FIG. 8, a ring shaped gap which isstill visible there but is actually smaller still remains there betweenthe end of the diffuser 31 and the flange 60 in order to make use of theelastic properties of the O-rings 62 for vibration damping.

A further flange 50, to which the tube plate 30 of the tube bundle and afurther exhaust gas collecting box 51 have been attached, has beenformed at the other end of the housing 11. In addition, connectors 52are formed on the housing 11 in order to be able to attach the exhaustgas heat exchanger to a connecting structure (not shown). Finally,connectors 70 have also been provided on the housing 11 in order toallow the coolant to flow in and out of the coolant ducts 5 of the tubebundle.

FIGS. 5-6 show that similar effects can also be achieved by the use ofone (or more) clamping elements 40 which can replace the sprung metallichook-shaped protrusions 12 or the springs or the like, but could alsosupplement them. The clamping element 40 can be a bolt which extendsthrough the bundle between the tubes 2 and connects housing walls lyingopposite. Rubber rings 41 or the like can be inserted in order to dampthe vibrations.

FIG. 10 shows curved springs 12 b or similar elements which are attachedbetween two grid-like, metallic securing structures 10. The curvature isalso embodied here in such a way that the insertion process can becarried out, during which process the springs 12 b yield elastically. Asis shown by FIG. 10, the springs 12 b which are arranged on oppositesides can also be arranged in an offset fashion, i.e. all four springsdo not need to lie in one plane which passes through the tube bundle.

It has become apparent that the present invention can allow thevibrations of the tube bundle in the housing to be overcome in such away that fractures and/or noise caused by them are avoided and/orsubstantially reduced.

An embodiment of a heat exchanger 101 according to the present inventionis shown in FIGS. 11-18 a. The heat exchanger 101 provides a flow path108 for a fluid to pass through the heat exchanger 101, wherein the flowpath 108 extends from a proximal end 111 of the heat exchanger 101 to adistal end 112 of the heat exchanger 101. The flow path 108 is enclosedwithin a casing 102, which can comprise multiple casing sections 103. Asfurther shown in FIG. 11, the casing 102 of the illustrated embodimentadditionally encloses flow paths 109 and 110, along which one or morefluids can be passed through the heat exchanger 101 so as to be placedin heat exchange relation with a fluid passing along the flow path 108.

Although FIG. 11 shows the flow paths 108 and 109 to be incounter-current flow orientation, it should be understood that in someapplications, other flow orientations (such as, for example, concurrentflow), may be preferred or equally suitable. Similarly, although flowpaths 108 and 110 are depicted as being in concurrent flow orientation,it should be understood that in some applications, other floworientations, such as, for example, counter-current flow, may bepreferred or equally suitable.

The fluid flow paths 108, 109 and 110 of the illustrated embodiment areat least partially defined by first and second heat exchange cores 104and 105, shown generically in FIG. 12. Each heat exchange core 104, 105of the heat exchanger 101 shown in FIG. 11 has a construction as shownin FIG. 12 (although adapted in length as needed to match the casings103 a, 103 b into which the cores 104, 105 are received, as necessary).Each of the cores 104, 105 include a bundle of parallel heat exchangetubes 106 extending between a first header 107 and a second header 120.Ends of the tubes 106 are sealingly attached to the headers 107, 120,such as by brazing, welding, or in any other suitable manner.Cylindrical flow conduits 121 are provided at that end of the core 105where the tubes 106 are attached to the header 120, to at leastpartially define another portion of the fluid flow path 108 downstreamor upstream of the portion defined by the heat exchange tubes 106. Itshould be understood that, although the exemplary embodiment depictsfour of the cylindrical flow conduits 121, the number of flow conduitspresent in a given application may be less than or more than four,without limitation.

The heat exchange cores 104, 105 further may include one or more baffles140 arranged along the length of either or both heat exchange cores 104,105. Such baffles 140 can provide benefit during assembly of the heatexchange cores 104, 105 by maintaining desired spacing between the tubes106. In some embodiments, the baffles 140 can define a tortuous portionof the flow path 109 or 110 over the outer surfaces of the heat exchangetubes 106 in order to increase the rate of heat transfer between fluidstraveling over and through the tubes. Alternatively or in addition,fluid flow plates (not shown) can be included between adjacent heatexchange tubes 106 in order to direct a fluid flowing along the flowpath 109 or 110.

In some embodiments, the heat exchange cores 104, 105 can include springplates 136 around one or more of the outer surfaces of the bundles oftubes 106. The utility of these spring plates 136 will be discussed indetail below. In some cases, one or more of the spring plates 136 can beattached directly to one or more of the baffles 140. Alternatively or inaddition, one or more of the spring plates 136 can be attached to straps139 (see FIGS. 12, 16 and 20) at least partially wrapped around one ormore of the heat exchange tubes 106, and/or other structure locatedadjacent, between, or around the heat exchange tubes 106. In theillustrated construction, attachment structure similar to that providedby the baffles 140 is connected to the strap 139 to attach the springplate(s) 136 to the strap 139.

It should be readily apparent to those having skill in the art that theheat exchange tubes 106 can take many different forms. In someembodiments, such as that shown in FIG. 12, the tubes 106 can be flattubes having first and second opposing substantially flat and long wallsconnected with relatively short (and in some cases, arcuately shaped)walls. In other embodiments, the tubes 106 can have a more rectangularshape, as shown in FIG. 13. In still other embodiments, the tubes 106can have a circular cross-sectional shape, or can be constructed fromtwo or more stacked plates. Also, in some embodiments, one or more ofthe heat exchange tubes 106 include an insert 141 (shown in FIG. 13)floating within or bonded to the inner walls of the tubes 106 to improvethe rate of heat transfer to or from fluid traveling through the tubes106.

While the cores 104, 105 for a given heat exchanger 101 may be identicalto one another in some cases, it should be understood that there is norequirement for them to be identical. In some cases, the cores 104, 105can differ in a variety of ways, including but not limited to tubelength, tube size, number of tubes, arrangement of tubes 106, and thelike.

Turning now to FIGS. 14-15, certain aspects of a casing section 103 willbe discussed. Although the specific casing section 103 shown in FIGS.14-15 corresponds to the casing section 103 b in FIG. 11, it should beunderstood that certain features shown in FIGS. 14-15 can similarly befound in the casing section 103 a of FIG. 11.

The casing section 103 of FIGS. 14-15 includes a first opening 137 at afirst end of the casing section 103, and a second opening 138 at asecond end opposite the first end. The opening 137 can be sized toaccommodate the entirety of a core 104 or 105 (in some cases, withoutthe header plate 107). The opening 138 can be smaller than the opening137, and can be sized to at least accommodate the one or morecylindrical flow conduits 121 of a core 104 or 105.

The illustrated casing section 103 further includes a plurality offastening locations 126 at the second end. These fastening locations 126can be located in a flange 117 at the second end. While the specificfastening locations 126 shown in the accompanying figures are depictedas circular through-holes, it should be understood that any otherassembly features suitable for assembling casing sections can besimilarly substituted. For example, the fastening locations 126 can, insome cases, take the form of pins, V-band grooves, blind threaded holes,etc.

The casing section 103 can include a pocket 116 at the second end. Insome embodiments, the pocket 116 is defined by a planar wall 114 inwhich the opening 138 is located, and by one or more walls 115 boundingthe outer periphery of the planar wall 114. In other embodiments, thepocket 116 can be defined by other portions of the casing while stillproviding a recess open to and facing away from the rest of the casingsection 103, and can be wider, thinner, deeper, or shallower as desired.Additionally, the casing section 103 may optionally include a groove 127at the second end, with the opening 138 at least partially enclosed bythe groove 127. In those embodiments in which both a pocket 116 and agroove 127 are present, the groove 127 can encircle the pocket 116, asshown in FIG. 15.

In some embodiments, the casing section 103 includes one or more of thefollowing: an inlet 133 to receive a fluid traveling along the flow path109 into the heat exchanger 101; an outlet 134 to remove a fluidtraveling along the flow path 9 from the heat exchanger 101; an inlet131 to receive a fluid traveling along the flow path 110 from the heatexchanger 101; and an outlet 132 to remove a fluid traveling along theflow path 110 from the heat exchanger 101. A casing section 103 can alsoinclude a flow conduit 154 to allow a fluid traveling along one of theflow paths 109, 110 to transfer from the casing section 103 to anothercasing section 103 without exiting the heat exchanger 101. Such a flowconduit 154 can, if present, be advantageously disposed within theboundaries of the groove 127, if present.

Heat exchange cores 104, 105 can each be assembled into respective onesof the casing sections 103 a and 103 b, as shown in FIG. 16. A core 104or 105 can be inserted into a casing section 103 by passing the core104, 105 through the opening 137 of the respective casing section 103 a,103 b, starting with the cylindrical conduits 121, until the header 107of the core 104, 105 reaches the casing section 103 a, 103 b,respectively. Spring plates 136 assembled to outer surfaces of the core104, 105 can be used to locate the core 104, 105 within the casingsection 103 a, 103 b by engaging with, and sliding along, one or moreinner surfaces 113 of the casing section 103 a, 103 b. The spring plates136 can have a suitable compliancy such that they can deform to allowfor contact between all of the spring plates 136 and their correspondingadjacent walls 113. This allows the core 104, 105 to be firmly containedwithin the respective casing section 103 a, 103 b in order to withstandshock and/or vibration loadings that may be experienced during operationof the heat exchanger 101, even when the inner surfaces 113 of thecasing sections 103 a, 103 b are uneven, and/or have varying surfacesresulting from production variations and manufacturing tolerances (e.g.,in casting processes).

Once the heat exchange core 104, 105 is so assembled into the respectivecasing section 103 a, 103 b, the header 107 of the core 104, 105 can befastened to the end of the casing 103 in a leak-tight fashion. In someembodiments, this fastening is achieved through the use of mechanicalfasteners, such as, for example, bolts that extend through holes 157found in the header 107 and into corresponding threaded holes 156 in theend of the casing 103 a, 103 b. A gasket (not shown) can be placed intoa groove 155 or can be otherwise installed at another suitable featureat the mating face of the casing 103 a, 103 b either during or prior toassembly in order to effect a leak-free joint between the header 107 andthe casing 103 a, 103 b. In other cases, a leak-free joint can insteadbe achieved by welding the header 107 to the casing 103 a, 103 b alongthe entire periphery of these elements.

It should be appreciated that assembling the core 104, 105 into thecasing section 103 a, 103 b as described allows for the location ofcylindrical flow conduit(s) 121 of the core 104, 105 to vary within thecasing section 103 a, 103 b, since that location will be dictated by thebearing of the spring plates 136 on the inner casing walls 113.

A sealing plate 118 (shown in greater detail in FIG. 17) is assembledonto the end of the heat exchange core 104, 105 by insertion of thecylindrical flow conduits 121 through corresponding apertures 128 in thesealing plate 118. A sealing gasket 122 (shown in FIGS. 8 a-8 b), suchas an O-ring, can be placed into a groove 129 located within each of theapertures 128 in order to achieve a fluid-tight seal between thecylindrical flow conduits 121 and the sealing plate 118. In embodimentsin which a plurality of cylindrical flow conduits 121 are used,excellent registration between the sealing plate 118 and the cylindricalflow conduits 121 can be achieved, owing to the unitary construction ofboth the sealing plate 118 and the end portion of the core 104, 105containing the cylindrical flow conduits 121, despite the variablelocation of the core 104, 105 within the casing 103 a, 103 b.

When the casing section 103 a, 103 b includes a pocket 116 as describedabove, the sealing plate 118 can advantageously be received into thepocket 116 such that assembly of the sealing plate 118 does not increasethe overall length of the heat exchanger 101. The pocket 116 can belarger than the sealing plate 118 so that a sufficient clearance gap isprovided between the peripheral walls 115 of the pocket and the sealingplate in order to allow for variability in the location of thecylindrical flow conduits 121 within the pocket 116.

The heat exchange cores 104, 105 can both be assembled into respectivecasing sections 103 a, 103 b as described above, and the casing sections103 a and 103 b can be joined together at the fastening locations 126 ofthe casing sections 103 a, 103 b. As shown in FIG. 18 a, assembling ofthe casing sections 103 a and 103 b can mate the end faces 135 (seealso, FIG. 15) of the flanges 117 of the casing sections 103 a, 103 bagainst one another. A sealing gasket 124 can also be provided in agroove 127 of at least one of the casing sections 103 a, 103 b in orderto create a leak-tight seal between the casing sections 103 a, 103 b, orcan otherwise be retained in place between the casing sections 103 a,103 b for this purpose. Also shown in FIG. 18 a are additional gaskets123 located in grooves 130 found in at least one face of the sealingplate 118. Assembly of the casing section 103 a to the casing section103 b can cause the sealing plates 118 a (assembled to one of the cores104, 105) and 118 b (assembled to the other of the cores 104, 105) tocontact each other and compress the gaskets 123 against the walls 114 inorder to create a leak-tight seal. The fluid-tight seals created by thegaskets 122, 123, and 124, alone or in combination, can prevent fluidcommunication between fluids traveling along the flow paths 108, 109,and 110, and can similarly prevent leakage of those fluids out of theheat exchanger 101.

Since the location of the cylindrical flow conduits 121 of each of thecores 104, 105 can be allowed to vary relative to the casing section 103a, 103 b into which the core 104, 105 is assembled, the apertures 128 ofthe sealing plate 118 a may not be directly aligned with the apertures128 of the sealing plate 118 b. However, such non-alignment will notresult in the loss of sealing between the fluid streams.

Once the heat exchanger 101 is so assembled, a continuous flow path 108is defined from the proximal end 111 of the heat exchanger 101 to thedistal end 112. The flow path 108 includes a first (upstream) sectiondefined by the tubes 106 of the core 104, extending from the inletheader 107 of the core 104 to the outlet header 120 of the core 104, andfurther includes a second (downstream) section defined by the tubes 106of the other core 105, extending from the outlet header 120 of the core105 to the inlet header 107 of the core 105. A third intermediatesection of the heat exchanger 101 is defined by a flow transitioningstructure 159 fluidly connecting the upstream and downstream sectionsjust described. The flow transitioning structure 159 extends from theheader 120 of the first core 104 to the header 120 of the second core105.

In some embodiments, the ends of the tubes 106 at both the proximate end111 and the distal end 112 of the heat exchanger 101 are rigidlyattached to the casing 102 by the attachment of the headers 107 to thecasing sections 103 a and 103 b. In other words, this attachment betweenthe tube ends 106 and headers 107, and the casing 102 is substantiallyinflexible, and does not permit relative movement between the tube ends106 and headers 107 and the casing 102. In a similar way, in someembodiments, the flow transitioning structure 159 is rigidly attached(or is relatively inflexible, and does not permit relative movement) ateither end to the ends of the tubes 106, by way of the headers 120. Incontradistinction, the two ends of the flow transitioning structure 159are flexibly connected to one another (indirectly through the sealingplates 118 a, 118 b) and to the casing 102, and/or are permitted toshift or otherwise move (in at least one direction, and/or at leastduring thermal expansion of the tubes 106 with respect to the casing102) based upon the manner in which the flow transitioning structure 159is assembled. Since the gaskets 122 provide a sliding seal for thecylindrical flow conduits 121 (as is required to enable assembly of thesealing plate 118 over the cylindrical flow conduits 121), and thecylindrical flow conduits 121 of core 104 can be separated from those ofcore 105 by a gap 158, the tube ends attached to the header 120 ofeither core are not prevented from displacing some amount in thetube-axial direction, and stresses at the tube-to-header joints by suchdisplacement can be reduced or eliminated.

The flexible joint and/or relative movement enabled by the transitioningstructure 159 described above can be especially beneficial inapplications where a large thermal expansion differential exists, eitherbetween the tubes 106 of core 104 and the tubes 106 of core 105, orbetween the tubes 106 of either core and the casing 102, or both. Suchthermal expansion differences have been known to cause premature failureof heat exchangers by causing high stresses, especially attube-to-header joints. Consequently, the life of a heat exchanger 101constructed according to some embodiments of the present invention canbe beneficially enhanced.

Another embodiment of a heat exchanger 101 according to the presentinvention is illustrated in FIG. 18 b. In the embodiment of FIG. 18 b,the pocket 116 (see also, FIG. 15) is found only in one of the casingsections (103 b). A casing section 103 a′ lacking the pocket 116 hasreplaced the previous casing section 103 a. Additionally, the sealingplate 118 a has been replaced with a larger sealing plate 119, and thegasket 123 found in the previous sealing plate 118 a has been replacedwith a similar gasket 125. In the embodiment of FIG. 18 b, the sealingplate 119 is included in the joint between the flanges 117 of the casingsections 103 a′ and 103 b. The seal between fluid flowing along the flowpath 108 and fluid flowing along the flow path 110 in this embodimentcan be provided solely by the gaskets 122. The new gasket 125 canprevent leakage of fluid flowing along the flow path 110 to the outsideof the heat exchanger 101.

In some embodiments, the heat exchanger 101 can be provided as an EGRcooler for use in an EGR system 160, shown in FIG. 19. The EGR system160 can include an engine 143 having an intake manifold 144 and anexhaust manifold 145, a compressor 147 coupled to an expander 146, andan EGR valve 151. A portion 149 of the hot, pressurized exhaust flowproduced by the engine 143 is directed from the exhaust manifold 145 tothe expander 146. The exhaust flow 149 is expanded to a lower pressurein the expander 146, and the energy derived thereby is used to compressa fresh combustion air flow 148 in the compressor 147. The compressedair flow 148 is directed from the compressor 147 to the intake manifold144.

With continued reference to the embodiment of FIG. 19, another portion150 of the hot, pressurized exhaust flow produced by the engine 143 isrecirculated, by way of the EGR cooler 101 and the EGR valve 151, fromthe exhaust manifold 145 back to the intake manifold 144, where it iscombined with the compressed air flow 148. The recirculated exhaust flow150 passes through the EGR cooler 101 along the flow path 108 (describedabove), is cooled by a first coolant flow 152 passing through the heatexchanger 101 along the flow path 110 (described above), and is furthercooled by a second coolant flow 153 passing through the heat exchanger101 along the flow path 109 (also described above).

In some embodiments of the EGR system 160 according to the presentinvention, the coolant flows 152 and 153 can be recombined at some pointin the system. In still other embodiments, the coolant flows 152 and 153can belong to segregated coolant flow circuits. Also, in someembodiments, the coolant flow 153 enters the EGR cooler 101 at a lowertemperature than does the coolant flow 152, or the coolant flow 152enters the EGR cooler 101 at a lower temperature than does the coolantflow 153.

In some embodiments, the coolant flows 152 and 153 both comprise aconventional engine coolant such as water, ethylene glycol, propyleneglycol, other coolant, or any mixture of these coolants. Also, either orboth of the coolant flow 152 and 153 can comprise a working fluid for aRankine cycle waste heat recovery system.

FIG. 20 illustrates the spring plate 136 and attachment structure 170 inmore detail. The illustrated attachment structure 170 is a sled-likestructure having a base wall 174 positionable against an adjacent tubesurface and upstanding side walls 178. The strap 139 extends over thebase surface 174 and between the side walls 178 to connect theattachment structure 170 to the tube(s) 106.

The spring plate 136 and the attachment structure 170 includecooperating attachment features to connect the spring plate to theattachment structure 170. Each side wall 178 includes a series ofprojections 180 and recesses 182, and the central projection 180 definesan axial hole 184. Each side wall of the spring plate 136 includes acorresponding series of projections 186 and recesses 188. Theillustrated recesses 188 include open-ended slots 188 a and closed holes188 b. The spring plate 136 also includes pin members 190 havingaxially-extending portions.

To assemble the spring plate 136 to the attachment structure 170, thespring plate 136 is positioned with each projection 180 on the sidewalls 178 of the attachment structure 170 being received in theassociated recess 188 and with each projection 186 on the spring plate136 being received in the associated recess 182 on the side wall 178.The spring plate 136 is moved in an axial direction (relative to thetubes 106) opposite to the direction of insertion of the bundle of tubes106 into the casing 102 to insert each pin member 190 into theassociated hole 184 on the side walls 178. When assembled, the springplate 136 is substantially held in position on the tube(s) 106 in theaxial and both transverse directions.

It should be understood that, in other constructions (not shown), thespring plate 136 and the attachment structure 170 may include differentattachment features. Also, different attachment structure may beprovided. In addition, in other constructions (not shown), the springplate 136 may be held in position in less than all of the axial and bothtransverse directions.

Various alternatives to the features and elements of the presentinvention are described with reference to specific embodiments of thepresent invention. With the exception of features, elements, and mannersof operation that are mutually exclusive of or are inconsistent witheach embodiment described above, it should be noted that the alternativefeatures, elements, and manners of operation described with reference toone particular embodiment are applicable to the other embodiments.

Embodiments described above and illustrated in the figures are presentedby way of example only and are not intended as a limitation upon theconcepts and principles of the present invention. As such, it will beappreciated by one having ordinary skill in the art that various changesin the elements and their configuration and arrangement are possiblewithout departing from the spirit and scope of the present invention.

What is claimed is:
 1. A heat exchanger comprising: a bundle of tubesinserted into a tubular housing, wherein exhaust gas flows through thetubes; a coolant duct arranged between the tubes; at least one grid-likesecuring structure which supports the bundle in the housing; and anoutwardly curved, metallic spring coupled to the bundle of tubes, thespring force of the spring being directed against the housing in orderto reduce vibrations; wherein the spring has a plate-like configurationincluding opposite side walls extending generally transverse to an axisof the bundle of tubes and opposite end walls extending generallyparallel to the axis, the side walls having a length greater than alength of the end walls.
 2. The heat exchanger of claim 1, wherein thespring is coupled to the grid-like securing structure to thereby couplethe spring to the bundle of tubes.
 3. The heat exchanger of claim 2,wherein the spring is coupled to two grid-like securing structures tothereby couple the spring to the bundle of tubes.
 4. A heat exchangercomprising: a bundle of tubes inserted into a tubular housing, whereinexhaust gas flows through the tubes; a coolant duct arranged between thetubes; at least one grid-like securing structure which supports thebundle in the housing; and an outwardly curved, metallic spring coupledto the bundle of tubes, the spring force of the spring being directedagainst the housing in order to reduce vibrations; wherein the spring iscoupled to the grid-like securing structure to thereby couple the springto the bundle of tubes; wherein one of the spring and the grid-likesecuring structure defines a recess and the other of the spring and thegrid-like securing structure includes a projection, the projection beingreceived in the recess to couple the spring to the grid-like receivingstructure.
 5. The heat exchanger of claim 1, wherein the spring iscoupled to the bundle of tubes in spaced relation from the grid-likesecuring structure.
 6. The heat exchanger of claim 5, and furthercomprising a strap extending at least partially around at least one ofthe bundle of tubes, and wherein the spring is coupled to the strap. 7.The heat exchanger of claim 1, and further comprising an outwardlycurved, metallic second spring coupled to the bundle of tubes, thespring force of the second spring being directed against the housing inorder to reduce vibrations, the second spring being spaced from thefirst-mentioned spring.
 8. The heat exchanger of claim 7, wherein thesecond spring is spaced from the first-mentioned spring along an axis ofthe bundle of tubes.
 9. The heat exchanger of claim 7, wherein thebundle of tubes has a first side and a different second side, wherein afirst-mentioned spring is arranged on the first side of the bundle oftubes, and wherein a second spring is arranged on the second side of thebundle of tubes.
 10. The heat exchanger of claim 9, wherein the firstside and the second side are adjacent sides of the bundle of tubes. 11.The heat exchanger of claim 1, wherein the bundle is a stainless steelsoldered structure, and wherein the housing is formed of aluminum and isa cast part into which the bundle is inserted.
 12. A heat exchangercomprising: a bundle of tubes inserted into a tubular housing, whereinexhaust gas flows through the tubes; a coolant duct arranged between thetubes; at least one grid-like securing structure which supports thebundle in the housing; and an outwardly curved, metallic spring attachedto the bundle of tubes, the spring force of the spring being directedagainst the housing in order to reduce vibrations; wherein a fluid flowpath extends between a first end and a second end of the housing,wherein the first-mentioned bundle of tubes has a first end and a secondend and defines a first section of the fluid flow path, and wherein theheat exchanger further comprises: a first header plate rigidly attachingthe first end of the bundle tubes to the first end of the housing; asecond bundle of tubes having a first end and a second end and defininga second section of the fluid flow path; a second header plate rigidlyattaching the second end of the second bundle tubes to the second end ofthe housing; and a third section of the fluid flow path fluidlyconnecting the first and second sections of the fluid flow path andincluding a sealing plate having one or more apertures for the fluidflow path to pass therethrough, the second end of the first-mentionedbundle of tubes being movable in at least one direction with respect tothe housing and the second bundle of tubes, the first end of the secondbundle of tubes being movable in at least one direction with respect tothe housing and the first-mentioned bundle of tubes.
 13. The heatexchanger of claim 4, wherein the spring has a plate-like configurationincluding opposite side walls extending generally transverse to an axisof the bundle of tubes and opposite end walls extending generallyparallel to the axis, the side walls having a length greater than alength of the end walls.
 14. The heat exchanger of claim 4, wherein thespring is interlinked with two grid-like securing structures to therebycouple the spring to the bundle of tubes.
 15. The heat exchanger ofclaim 4, further comprising an outwardly curved, metallic second springcoupled with the bundle of tubes, the spring force of the second springbeing directed against the housing in order to reduce vibrations, thesecond spring being spaced from the first-mentioned spring.
 16. The heatexchanger of claim 15, wherein the second spring is spaced from thefirst-mentioned spring along an axis of the bundle of tubes.
 17. Theheat exchanger of claim 15, wherein the bundle of tubes has a first sideand a different second side, wherein a first-mentioned spring isarranged on the first side of the bundle of tubes, and wherein a secondspring is arranged on the second side of the bundle of tubes.
 18. Theheat exchanger of claim 17, wherein the first side and the second sideare adjacent sides of the bundle of tubes.
 19. The heat exchanger ofclaim 4, wherein the bundle is a stainless steel soldered structure, andwherein the housing is formed of aluminum and is a cast part into whichthe bundle is inserted.